CN101903663A - Clutch end-of-fill detection strategy related solenoid valve - Google Patents
Clutch end-of-fill detection strategy related solenoid valve Download PDFInfo
- Publication number
- CN101903663A CN101903663A CN2008801216947A CN200880121694A CN101903663A CN 101903663 A CN101903663 A CN 101903663A CN 2008801216947 A CN2008801216947 A CN 2008801216947A CN 200880121694 A CN200880121694 A CN 200880121694A CN 101903663 A CN101903663 A CN 101903663A
- Authority
- CN
- China
- Prior art keywords
- clutch
- pressure
- solenoid valve
- topping
- valve body
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
Images
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F15—FLUID-PRESSURE ACTUATORS; HYDRAULICS OR PNEUMATICS IN GENERAL
- F15B—SYSTEMS ACTING BY MEANS OF FLUIDS IN GENERAL; FLUID-PRESSURE ACTUATORS, e.g. SERVOMOTORS; DETAILS OF FLUID-PRESSURE SYSTEMS, NOT OTHERWISE PROVIDED FOR
- F15B13/00—Details of servomotor systems ; Valves for servomotor systems
- F15B13/02—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors
- F15B13/04—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor
- F15B13/042—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure
- F15B13/043—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure with electrically-controlled pilot valves
- F15B13/0433—Fluid distribution or supply devices characterised by their adaptation to the control of servomotors for use with a single servomotor operated by fluid pressure with electrically-controlled pilot valves the pilot valves being pressure control valves
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Control Of Transmission Device (AREA)
Abstract
A system and method for controlling a hydraulic transmission (10) uses a solenoid valve (12) having a pressure sensor linked to the valve body (20) operable to sense a hydraulic fluid pressure within a cavity (33) of the valve body (20) and to transmit an electrical signal based on the sensed pressure. The transmitted signal is used to identify the end of fill time, and thus to end a clutch fill phase and commence a clutch modulation or lock-up phase.
Description
Technical field
The present invention relates generally to and can carry out the firm clutch topping up control and the system and method for hydraulic pressure correction transmission clutch, more specifically, relates to the system and method that is used for proofreading and correct at the speed changer of Clutch Control pressurized operation MEDIA FLOW.
Background technique
Hydraulic coupling is generally known and can finding in a lot of systems and device.In a kind of enforcement, use cover (a plurality of) hydraulic coupling help speed changer different I/O gears than or gear than scope between gear shift.In general, the speed changer set that generally includes input shaft, output shaft and can be used in some the relevant teeth parts for example arranged with planetary pinion mode or other modes that optionally connect input shaft and output shaft.Clutch can be used for selecting the gear ratio and selecting gear to compare scope in stepless speed variator at discrete speed changer.Here, two kinds of coupled type all will be called as " speed ratio ".
The selection of the gear ratio at output shaft place is to carry out by the rotation that influences teeth parts and/or one or more clutches of correlation.Clutch normally hydraulic actuating with splicing tpae class or dish class torque transfering element.From a gear than transform to another gear than relate generally to with current gear than be associated one or more be about to holdback clutchs (off-goingclutch) discharge or separates and will with the gear of hope than one or more engaging clutches (on-coming clutch) application or the joints of being about to that are associated.For instance, though in this speed changer, can use a lot of different clutches to arrange that a kind of possible layout is the double clutch shift transmission.In this layout, need two clutches to keep the specific gear in the described speed changer.Usually, need main clutch, the clutch element that main clutch normally rotates keeps main clutch to be used for being about to the gear of use; And inferior clutch, separate time clutch to shift into the gear that is about to use.The inferior clutch that is used for this gear shift situation in the art is also referred to as holdback clutch soon.This clutch is substituted by new, " being about to engage " clutch, needs to be about to engaging clutch and uses new gear to impel speed changer.In other words, single by making " be about to throw off " clutch is not worked and is made single " being about to engage " clutch work and keep three-clutch to be used for carrying out gear shift with new gear originally.In other layout, use a plurality of being about to engage and/or be about to holdback clutch, increased the complexity and the significance of clutch actuation timing.
Each hydraulic coupling drives by the electric control solenoid valve usually.This solenoid valve is regulated controlling to the hydraulic fluid pressure of clutch by electricity, thereby is controlled at the motion of the interim clutch plunger of clutch topping up.
The phase place that will soon engage and be about to the holdback clutch element can have remarkable influence to the shift quality of being felt.For example, if be about to the holdback clutch premature disengagement, before still being in interim being about to of topping up engaging clutch has enough torque capacity, engine speed may produce the vibration of short time so.In addition, if be about to the too early topping up of engaging clutch, before soon holdback clutch was ready to begin transmission of torque, clutch element had enough torque capacity so.This can cause the three-dimensional clutch stuck, can shorten the working life of speed changer under not serious situation, and cause the mechanical failure of speed changer usually under opposite extreme situations.On the contrary, under the situation that the clutch topping up postpones, be about to holdback clutch and engaging clutch soon passed in torque before having enough torque capacities being about to engaging clutch, and do not have time enough with the particular gear of suitable torque capacity locking because be about to engaging clutch, skid so speed changer can produce with the maintenance target.Final result is skidding of clutch friction plate, and this also is undesirable, because the excessive heat that can produce owing to the higher clutch relative velocity by the clutch friction plate that rotates causes producing the high clutch energy.Except forming offending user's experience, the bad gear shift of timing will be along with the efficient and the working life of time effects speed changer.Therefore, wishing accurately to activate speed changer makes realize level and smooth gear shift in the whole working life of speed changer in the whole operation velocity range of speed changer.
It is experimental but not simultaneously that the existing method that is used to proofread and correct transmission clutch is tended to.In other words, can observe the performance of the clutch when some points, and draw the conclusion that how to respond flow of pressurized about clutch.Use these to observe periodically " correction " clutch then.But the situation of clutch and the variation that operating environment can produce essence in the interval of proofreading and correct cause shift quality to descend.
The solution of the significant or inapparent shortcoming of prior art is wished that this solution does not form restriction crucial or essence to disclosed principle though the inventor has been found that.In addition, background technique partly is the reader understanding of being convenient to non-those skilled in the art.But, should be appreciated that the background technique part is very simple, be not meant to and accurately and intactly summarize prior art.Therefore, aforementioned background note is the explanation of simplifying of character for example, and is not meant to the reference that replaces related domain.Exist inconsistent between illustrated state of reference and the above stated specification or the situation of omitting under, above stated specification is not meant to corrects that these are inconsistent or omit.The claimant tends to the illustrated state of prior art reference.
Summary of the invention
In one aspect, the present invention relates to a kind of method that is used to control speed changer, this speed changer has a plurality of hydraulic couplinges that are used for gear shift between one or more velocity ratios.Aspect this, thereby this method comprises that being about to the holdback clutch element by instruction reduces hydraulic pressure and flow to the separation of beginning clutch and instruction hydraulic fluid and be about to engaging clutch is carried out speed changer with the clutch chamber that is full of second described hydraulic coupling gear shift.This method comprises that also detection pressure greater than predetermined amplitude in the chamber of second hydraulic coupling rises, and determines that based on the pressure rising that is detected clutch chamber is filled.Thereby starting clutch is regulated the phase and is about to the engagement hydraulic clutch to engage fully, makes it to receive transmission of torque fully from being about to the holdback clutch element.
In yet another aspect, the present invention relates to be used to control the control system of speed variator of speed changer with a plurality of hydraulic couplinges.This system comprises the gearbox controller that is used to control to engaging clutch soon and is about to the flow of hydraulic fluid of holdback clutch, and " solenoid valve " that be associated with each clutch.Each solenoid valve has the coil part that is connected with gearbox controller, and coil part can be used in the flow of hydraulic fluid of control by solenoid valve.The pressure transducer that each solenoid valve also comprises fluid input, fluid output and is fixed to solenoid valve and is communicated with outlet and clutch chamber fluid.Pressure transducer in can the sensing solenoid valve pressure and will represent that the signal of the pressure of institute's sensing is sent to gearbox controller so that the operation of gearbox controller correction solenoid valve.
In yet another aspect, the present invention relates to a kind of solenoid valve that is used for hydraulic transformer, this solenoid valve comprises the spring of valve body, spool, bias voltage spool and the pressure chamber of bias voltage spool in the opposite direction.Solenoid valve also comprises inlet, exports and is connected to the pressure transducer of valve body, and this pressure transducer can be operated with the hydraulic fluid pressure in the chamber of sensing valve body and based on the pressure of institute's sensing and send electrical signal.
Description of drawings
Fig. 1 is the sectional schematic of the hydraulic coupling can principle according to the present invention controlled;
Fig. 2 is the schematic diagram according to the hydraulic clutch control system of principle of the present invention;
Fig. 3 is the sectional view according to the electric hydraulic coupling pressure controlled valve of principle of the present invention;
Fig. 4 illustrates the desirable clutch pressure timing diagram that can principle according to the present invention be used to detect the hydraulic pressure peak value that topping up finishes; And
Fig. 5 is the flow chart that illustrates according to the process of principle control hydraulic coupling of the present invention.
Embodiment
The present invention relates to use the operation of hydraulic coupling with the speed changer of control velocity ratio or scope gear shift timing.Principle of the present invention provide a kind of be used to dispose with solenoidoperated cluthes make it possible to accurately know that thereby the topping up of clutch finishes to improve the mechanism of shift quality.Fig. 1 is the schematic diagram of the simplification of hydraulic coupling 1.Hydraulic coupling 1 generally includes cylinder 2, and cylinder 2 is defined for the chamber 3 that keeps hydraulic fluid.Chamber 3 also comprises piston 4 or other movable members that cooperation ground is installed, and is used for hydrodynamic pressure is passed to friction member 6 from the extension 5 that is associated, and for example clutch friction plate piles up.The level of the fluid volume in chamber 3 makes friction member 6 move to its final position, the piling up and contact fully of clutch friction plate for example with its staggered transmitting element (not shown), and clutch 1 is called as " being full of ".Between the emptying and full state of clutch 1, piston 4 can move for example distance of the weak point of about 4mm.
In case clutch 1 is full of, fluid continues to introduce chamber 3 and will cause the pressure in the chamber 3 to rise.This causes fluid that the active force of piston 4 is increased, and correspondingly makes friction increase between friction member 6 and its corresponding component (for example and its staggered transmitting element).When certain stress level (can be unique for clutch 1), frictional force between friction member 6 and its corresponding component overcomes the resistance of the load (for example machine speed changer etc.) that is connected to corresponding component fully, and clutch 1 " locking " makes friction member 6 and corresponding component thereof move jointly and torque is transmitted fully by clutch 1.
Under the environment of multi-clutch speed changer, the timing of clutch locks and release is very important.For example, before holdback clutch release soon, lock, may cause speed changer or machine are produced serious damage if be about to engaging clutch.Even avoided damage, the operator of machine may feel still that also gear shift is rough and uncomfortable.
Usually, the specific and time point that rule of thumb determine of clutch 1 clutch that is considered to be full of be used to fluid to the chamber 3 introducing change into another kind of pattern (promptly tilting the phase) from a kind of pattern (being pulse period).Therefore, the timing that is full of a little is very important for shift quality.As indicated above, because by giving chamber 3 equipment apparatuses to detect actual difficulty and other the relevant obstacles that is full of a little, existing clutch timing scheme is used being full of a little of estimating.In a kind of mode of execution of principle of the present invention, use a kind of system of novelty to detect being full of of clutch in real time, thereby avoid existing static system intrinsic estimation and correction error.
In one embodiment, mechanical transmission system 10 uses one or more electric hydraulic coupling pressure control (ECPC) valve.Exemplarily be illustrated in an example of the ECPC valve 12 in the operating environment of general transmission system 10 among Fig. 2.In the example that illustrates, ECPC valve 12 is from receiving the input of compression fluid such as the fluid source of oil hydraulic pump 11.Here compression fluid is illustrated as hydraulic fluid; But, it will be understood by those skilled in the art that any fluid that the enforcement that can satisfy in the given system requires all is fit to.
Electric control signal so that movable valve plug that ECPC valve 12 receives such as the curtage signal from gearbox controller 13, thus cause ECPC valve 12 to provide fluid output to clutch 1 with the pressure of setting by control signal.Like this, gearbox controller 13 can be controlled the hydrodynamic pressure that offers clutch, thus and the operation of solenoidoperated cluthes.In one embodiment, gearbox controller 13 solenoidoperated cluthes 1 make that topping up is to avoid finishing a little rough " contact (touch up) " at topping up when one or more first predetermined pressure for clutch, and clutch pressure rises to such as basically greater than one or more second predetermined pressures of one or more first predetermined pressures then.Like this, in case clutch chamber is full of and clutch is ready to transmitting torque, gearbox controller 13 beginning clutches are regulated so that clamping force maximizes, thereby make clutch be ready to enter the transmission of torque phase.
As mentioned above, the timing of clutch transformation may influence the shift quality between velocity ratio greatly.Be converted to the pressure (i.e. " clutch locks pressure ") that is suitable for lock-up clutch 1 in order to determine when more accurately from the pressure (i.e. " clutch supercharging pressure ") that is suitable for being full of clutch 1, gearbox controller 13 definite clutches 1 have been finished the time point (i.e. " topping up is finished a little ") of topping up.In an example, gearbox controller 13 determines that by the pressure of hydraulic fluid in pressure switch or the transducer monitoring ECPC topping up finishes a little.Especially, have been found that at topping up and finish a little that fluid pressure disturbances feeds back to ECPC valve 12 from clutch 1, and utilize this disturbance to finish a little accurately to distinguish topping up.
Exemplarily show the enforcement of the ECPC consistent among Fig. 3 with this discovery.Generally speaking, the ECPC valve 12 among Fig. 3 comprises the valve body 20 with a plurality of holes and chamber, and a plurality of holes and chamber are arranged to the pressurized hydraulic fluid flow of regulating the outlet 22 from source inlet 21 to clutch in response to solenoid 23.ECPC valve 12 comprises spool 24, spool under the effect of two power main body 20 internal linear move the power of power that these two power are pressure spring 25 and the relative displacement that causes by pressure chamber 26.
Solenoid 23 is included in the actuator 27 in the coil unit 28.When energising, coil unit 28 is at least roughly being that the power of function of electric current that for example puts on the coil unit 28 of solenoid 23 by electronic control module (ECM) (as gearbox controller 13) forces actuator 27 towards main body 20.Along with actuator 27 is forced to towards main body 20, the retainer 29 on the actuator 27 is cooperated with hole, pressure chamber 30 to regulate the 26 fluid streams that flow out from the pressure chamber.This again regulating action in spool 24 overcoming the hydraulic coupling of pressure spring 25, thereby regulate the linear position of main body 20 inner spools 24.
Along with spool 24 in main body 20 when mobile, the columniform projection 31 on the spool 24 is cooperated with the face 32 on the main body 20 and is entered the introducing that exports the fluid of the valve pumping chamber 33 that 22 fluids are communicated with clutch to regulate from source inlet 21.Because illustrated interaction, exporting the hydrodynamic pressure of supplying with at 22 places at clutch can control by the electric current that is put on the coil unit 28 of solenoid 23 by gearbox controller 13.This makes gearbox controller 13 can control the position and the pressure of the one or more clutches that are associated with ECPC valve 12.
But, as mentioned above, be difficult to the physical location of gaging clutch constituent elements with respect to its full engagement position (i.e. position when the complete transmitting torque of clutch).Like this, also be difficult to make soon engaging clutch and holdback clutch coordination soon, to avoid the gear shift action of suboptimization with enough accuracys.In order to overcome this shortcoming and to allow based on real time status but not historical data is formed parts to clutch and located in real time, ECPC valve 12 also comprises the pressure switch 34 that is communicated with valve pumping chamber 33 fluids.Pressure switch 34 for example can be switch over the ground (SWG) input of energy normal open (closure) or normal off (opening).
Pressure switch 34 is connected so that one or more electrical signal are sent to controller with gearbox controller 13.In response to the signal that is sent, gearbox controller 13 changes its mode of giving solenoid 23 chargings so that gear shift timing optimization.Especially, switch 34 is finished the variation in pressure pattern of being scheduled in a little the valve pumping chamber 33 in response to expression clutch topping up.Topping up is finished some the range corresponding to piston 4, and when arriving this, and the volume of clutch chamber 3 arrives and maximumly also stops.Finish a place when clutch chamber 3 at topping up and stop expansion suddenly, the fluid that flows in system is because inertia continues to flow into fixing clutch chamber 3 with roughly the same speed at short notice.
This imbalance of flow causes that clutch chamber 3 instantaneous pressures rise or peak value when topping up is finished, and this pressure peak feeds back to the control side of ECPC valve 12.When topping up is finished pressure peak arrival ECPC valve 12, rise in the pressure short time in the valve pumping chamber 33, and switch 34 detects this rising.At this moment, switch 34 will represent that the signal of pressure peak is sent to gearbox controller 13, and gearbox controller 13 is finished the signal interpretation that is sent a little for the expression topping up.
Observe, In one arrangement, topping up is finished the endurance that pressure peak can have the amplitude of about 10psi and continue about 4ms.Therefore, in this embodiment, hope is used at 10psi or is lower than the switch that 10psi is triggered.But, should be appreciated that between shift quality and sensor cost to have balance.The sharp cutting edge of a knife or a sword that needs is big more, and gear shift may be made an appointment with roughly.But the peak value that needs is more little, because resolution improves, the cost of sensor is high more.Simultaneously, the sensitivity of switch 34 should make that switch 34 can be owing to triggering such as the System noise that may have about 5psi or lower amplitude.The sensitivity of switch 34 may change according to enforcement.Especially, should be appreciated that the system that implements according to principle of the present invention, topping up is finished pressure peak may be greater than or less than 10psi, and system noise levels may be greater than or less than 5psi.
When the pressure peak endurance was about 4ms, switch 34 should have the enough fast response time to make response in the time of this grade.In addition, though a lot of ECM moved with the cycle time (carrying out the time lag of control flow) of about 10ms, this cycle time is oversize and be difficult to guarantee to observe pressure peak.Especially, if pressure peak occurs between circulation, just possibly can't detect.Therefore, in one embodiment, be about 2.5ms or lower the cycle time of gearbox controller 13, to guarantee that pressure peak no matter when occurring can both detect.
Even noted switching response time and sensitivity and 13 cycle times of gearbox controller, still might the clutch pressure peak value be detected or wrong triggering before the clutch pressure peak value occurring, occurs.For example, the clutch pressure peak value in the clutch chamber 3 may roughly side by side occur with another pressure surge source in the control side of relevant valve.In this case, the pressure peak of clutch chamber 3 may not intactly feed back to valve pumping chamber 33, therefore may not be detected.Therefore, in another mode of execution, gearbox controller 13 can stop the clutch topping up phase and begin clutch regulating the phase, promptly, in order to ensure transmission of torque and lock-up clutch 1, do not detect topping up if the clutch topping up phase has continued to surpass the rule of thumb predetermined specific amount of time of clutch and finish pressure peak.Predetermined amount of time depends on the enforcement environment, but in an example, predetermined amount of time is set to about 625ms.Should be appreciated that the clutch topping up time is the function of clutch volume and hydraulic fluid temperature and viscosity.
Similarly, for fear of the too early triggering of clutch 34, in an example, in the predetermined interval after the clutch topping up phase begins, do not use switch 34 or ignore its output.This guarantees at most of topping up interim, and the pressure surge that causes at the noise of the control side of related valves is trigger switch too early not.The size at predetermined interval depends on the enforcement environment, and in an example, predetermined amount of time is set to about 450ms.
Example Figure 40 of the pressure peak that the rising of expression pressure has been shown among Fig. 4 and has been correlated with.Should be appreciated that pressure switch 34 will sense the peak value 41 that illustrates, but can not sense the remainder of pressure diagram 42 usually.But, in one embodiment, can the working pressure sensor or transducer come place of switches 34, this sensor can detect a plurality of stress levels of pressure diagram 42 in this case.The hydraulic pressure of the control side (for example in valve pumping chamber 33) of pressure diagram 42 expression ECPC valves 12, and be illustrated in the topping up phase and begin 43 and finish a little 44 the relative constant compression force above the starting stage instantaneous pressure to topping up.Finish a little 44 at topping up, pressure peak for example rises to the grade of 10psi in described mode above.Peak value 41 is instantaneous, then along with the balance of the hydrodynamic pressure of control side and disappear.As indicated above, gearbox controller 13 uses these pressure to distinguish that topping up finishes, thereby and in the time period 45 beginning such as the next stage of the phase of adjusting.
The flow chart of Fig. 5 illustrates the exemplary process 50 that is used for carrying out according to the principle of above explanation clutch management, comprises that topping up finishes detection.For declarative procedure 50, the supposing the system structure is illustrated as Fig. 1 to Fig. 3.Also the machine speed changer discussed of hypothesis is carried out the double clutch gear shift.But these hypothesis only are for the ease of understanding, and desired situation in not all mode of execution.
In the stage 51 of process 50, gearbox controller 13 need to determine shifting of transmission.These needs may be because such as the increase of machine speed and/or load or reduce, or operator's action, for example situations such as the increase used of additional device or minimizing.In the stage 52, gearbox controller 13 sends hydraulic coupling reduction instruction to the holdback clutch that is about to that is associated with current velocity ratio.
Stage 53 is with the scheduled time with respect to the beginning in stage 52 (before, simultaneously or afterwards), in the stage 53, and the topping up phase of engaging clutch soon that gearbox controller 13 beginnings are associated with the velocity ratio of new hope.In one embodiment, the topping up phase comprises the instruction of sending the clutch supercharging pressure by solenoid 23.In the topping up phase, finish pressure peak to detect topping up at stage 54 gearbox controllers, 13 pilot switches 34.Simultaneously in the stage 55, gearbox controller 13 detects from the topping up phase and begins elapsed time.If determine to detect pressure peak or passed through predetermined amount of time in the topping up phase by switch 34 at stages 56 gearbox controller 13, gearbox controller 13 proceeds to the stage 57.Otherwise process 50 is back to parallel stage 54 and 55.
In the stage 57, gearbox controller 13 stops the topping up stage and begins clutch regulating the phase, promptly increases transmission of torque and lock-up clutch 1.This stage causes that usually clutch pressure increases, and no longer skids and complete transmitting torque until clutch.In case clutch 1 arrives locking, gear shift is finished.Should be appreciated that above-mentioned principle similarly is suitable for for each clutch under the situation of a plurality of engaging clutches soon and a plurality of holdback clutchs soon.
Industrial applicibility
The present invention is applicable to hydraulic transformer, that is, use hydraulic clutch with the speed changer of control gearratio or gear range gear shift timing. Especially, thus principle of the present invention provide a kind of for the configuration and solenoidoperated cluthes 1 so that accurately know clutch 1 topping up finish the improvement shift quality mechanism. This system can implement at highway or non-highway machine, construction machine, industrial machine etc. Although a lot of machines that can obtain advantage from principle of the present invention are the machines that is used at least once in a while transportation goods and materials, material or personnel, should be appreciated that hydraulic transformer also uses under other environment, and instruction of the present invention also has widely application similarly.
Utilize principle of the present invention, gearbox controller 13 (for example ECM) can determine that clutch has arrived the time point towards the extreme limit of travel that engages. Utilize then this to determine, gearbox controller 13 can be regulated clutch and begin accurately timing to avoid clutch 1 to cross evening or too early locking. In yet another aspect, disclosed system is provided at gearbox controller 13 because any reason does not detect the reserve mechanism in the situation of topping up deadline. Especially, in one embodiment, if begin to pass through the predetermined time section from the topping up phase, then gearbox controller 13 starting clutches are regulated the stage. In addition, because system noise may trigger the pressure switch 34 for detection of the topping up deadline, so in the predetermined time after the topping up phase the begins amount, controller can not use or ignore pressure switch 34.
Although example disclosed above is working pressure switch or transducer in each magnetic valve, this is not to carrying out the requirement of principle of the present invention. But should be appreciated that above-mentioned being taught under single pressure switch or transducer and the environment that a plurality of magnetic valves are associated also is suitable for. In one embodiment, pressure switch or transducer can carry out multiplexed between two or more magnetic valves.
Should be appreciated that above-mentioned explanation provides the example of system of the present invention and technology.But, can expect that other enforcement of the present invention may be different with above-mentioned example in detail.Usually, all references of the present invention or its example is intended to quote the specific example of being discussed at that time, scope of the present invention is carried out any restriction and be not meant to.Statement about all distinctivenesses of some features and the property criticized is intended to expression to the preferably use of these features, except as otherwise noted, does not represent these features are got rid of in scope of the present invention fully.
Here the explanation to the scope of value only is intended to drop on the stenography method that each the independent value in this scope is quoted separately with opposing, unless explanation is arranged here in addition, each independent value is included in the specification to illustrate similarly separately.Unless obviously contradiction of explanation and context is arranged here in addition, Shuo Ming all methods can be carried out with any suitable order here.
Therefore, according to applicable law, the present invention includes all corrections and the equivalence of the described theme of accompanying Claim book.In addition, unless obviously contradiction of explanation and context is arranged here in addition, any combination of all possible modification of said elements is included in the scope of the present invention.
Claims (9)
1. solenoid valve (12) that is used for hydraulic transformer (10), this solenoid valve (12) comprising:
Valve body (20);
Be positioned at the spool (24) of described valve body (20), wherein, described spool (24) is being limited at least one dimension and can moving in predetermined scope on another dimension;
Spring (25), it is with the first end biasing of described spool (24) towards the predetermined moving range of described spool;
Pressure chamber (26), it is formed between described spool (24) and the described valve body (20), is used to receive hydraulic fluid and is used for described spool (24) towards the biasing of second end of the predetermined moving range of described spool;
The outlet (22) that is used to receive the inlet (21) of pressurized hydraulic fluid and is used for pressurized hydraulic fluid is offered hydraulic coupling (1); And
Pressure transducer (34), it is connected to described valve body (20), and described pressure transducer can be operated with the hydraulic fluid pressure in the chamber (33) of the described valve body of sensing (20) and send electrical signal based on the pressure of institute's sensing.
2. solenoid valve according to claim 1 (12), wherein, the described chamber (33) of described valve body (20) is communicated with valve outlet port (22) fluid.
3. solenoid valve according to claim 1 (12), wherein, described pressure transducer (34) is the pressure switch that can be connected to gearbox controller (13).
4. solenoid valve according to claim 1 (12), wherein, described pressure transducer (34) is switch over the ground.
5. solenoid valve according to claim 1 (12), wherein, described pressure transducer (34) is a pressure transducer.
6. solenoid valve according to claim 1 (12) also comprises with described pressure chamber (26) linking with the actuator (27) of regulator solution hydraulic fluid from the outflow of described pressure chamber (26).
7. solenoid valve according to claim 1 (12), wherein, described spool (24) comprises the cylindrical projections (31) of cooperating and fluid being guided to described outlet (22) from described inlet (21) to regulate with the face (32) on the described valve body (20).
8. a hydraulic transformer system (10) comprises according to any described solenoid valve (12) in the claim 1 to 7.
9. a control is according to the method for any described solenoid valve (12) in the claim 1 to 7, comprises based on the electrical signal that is sent stopping the clutch topping up phase and the beginning clutch is regulated the phase.
Applications Claiming Priority (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| US11/963,204 US7909733B2 (en) | 2007-12-21 | 2007-12-21 | Clutch end-of-fill detection strategy |
| US11/963,204 | 2007-12-21 | ||
| PCT/US2008/013758 WO2009085151A1 (en) | 2007-12-21 | 2008-12-16 | Clutch end-of-fill detection strategy related solenoid valve |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN101903663A true CN101903663A (en) | 2010-12-01 |
Family
ID=40454128
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2008801216947A Pending CN101903663A (en) | 2007-12-21 | 2008-12-16 | Clutch end-of-fill detection strategy related solenoid valve |
Country Status (4)
| Country | Link |
|---|---|
| US (1) | US7909733B2 (en) |
| CN (1) | CN101903663A (en) |
| DE (1) | DE112008003449T5 (en) |
| WO (1) | WO2009085151A1 (en) |
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103122995A (en) * | 2011-11-18 | 2013-05-29 | 腓特烈斯港齿轮工厂股份公司 | Hydraulic valve system for actuating at least one shifting element of a transmission |
| CN103291906A (en) * | 2012-02-27 | 2013-09-11 | 腓特烈斯港齿轮工厂股份公司 | A method of determining an operating state of a form-locking shift element of a transmission apparatus |
| CN103477127A (en) * | 2011-04-19 | 2013-12-25 | 马自达汽车株式会社 | Automatic transmission control method and control device, and automatic transmission system |
| CN105889357A (en) * | 2015-02-17 | 2016-08-24 | 通用汽车环球科技运作有限责任公司 | Compensation for drag force generated by rotating clutch piston seal |
| CN106471270A (en) * | 2014-06-17 | 2017-03-01 | 沃尔沃卡车集团 | Improved clutch control |
| CN107091322A (en) * | 2016-02-18 | 2017-08-25 | 通用汽车环球科技运作有限责任公司 | Pressure sensor for power output |
Families Citing this family (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US8303463B2 (en) * | 2007-10-26 | 2012-11-06 | GM Global Technology Operations LLC | Method and apparatus to control clutch fill pressure in an electro-mechanical transmission |
| US8090512B2 (en) * | 2008-07-24 | 2012-01-03 | GM Global Technology Operations LLC | System and method for controlling a clutch fill event |
| US20100087999A1 (en) * | 2008-10-03 | 2010-04-08 | Gm Global Technology Operations, Inc. | Apparatus and Method for Detecting End-of-Fill at Clutch in Automatic Transmission |
| US8489297B2 (en) * | 2009-04-15 | 2013-07-16 | Caterpillar Inc. | Clutch hold level as a function of torque |
| US8615349B2 (en) * | 2009-11-11 | 2013-12-24 | GM Global Technology Operations LLC | Method of detecting filling of hydraulic clutch |
| US9194490B2 (en) * | 2010-10-15 | 2015-11-24 | GM Global Technology Operations LLC | Micro-electro-mechanical-systems based hydraulic control system for a wet dual clutch transmission |
| US20120158264A1 (en) * | 2010-12-21 | 2012-06-21 | Caterpillar Inc. | Clutch calibration for continuously variable transmission |
| US8965650B1 (en) * | 2013-10-14 | 2015-02-24 | GM Global Technology Operations LLC | System and method for controlling an automatic transmission |
| JP5928530B2 (en) * | 2014-06-18 | 2016-06-01 | トヨタ自動車株式会社 | Hydraulic transmission control amount generation device for automatic transmission and control device for automatic transmission |
| DE102014214253A1 (en) | 2014-07-22 | 2016-01-28 | Schaeffler Technologies AG & Co. KG | High flow switching valve with pilot unit |
| DE102014222082A1 (en) | 2014-10-29 | 2016-05-04 | Schaeffler Technologies AG & Co. KG | Self-sealing quick-acting valve |
| DE102016217865A1 (en) * | 2016-09-19 | 2018-03-22 | Bayerische Motoren Werke Aktiengesellschaft | Method and device for improving the shift quality of a motor vehicle with an automatic transmission |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5722459A (en) * | 1995-05-31 | 1998-03-03 | Hyundai Motor Company | Pressure control valve of a hydraulic control system of an automatic transmission |
| US5913577A (en) * | 1996-12-09 | 1999-06-22 | Caterpillar Inc. | Pilot stage of an electrohydraulic control valve |
| EP1285806A2 (en) * | 2001-08-10 | 2003-02-26 | Caterpillar Inc. | Power take-off clutch control system |
| US6796329B1 (en) * | 2002-01-23 | 2004-09-28 | Trans-A-Matic | Compact fluid pressure control valve solenoid with pilot or gate valve |
| CN1924387A (en) * | 2005-09-02 | 2007-03-07 | 通用汽车公司 | Clutch control regulator valve with end of fill detection |
| JP4806934B2 (en) * | 2005-01-31 | 2011-11-02 | アイシン精機株式会社 | Hydraulic control device for automatic transmission |
Family Cites Families (21)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5421912B2 (en) | 1971-12-02 | 1979-08-02 | ||
| US4465168A (en) | 1981-11-25 | 1984-08-14 | Kabushiki Kaisha Komatsu Seisakusho | Pressure control system for a transmission |
| JPH0719852Y2 (en) | 1988-03-30 | 1995-05-10 | 日産自動車株式会社 | Active suspension |
| US5046174A (en) | 1990-01-11 | 1991-09-03 | General Motors Corporation | Method of clutch-to-clutch closed throttle downshift in an automatic transmission |
| US5119695A (en) | 1991-06-27 | 1992-06-09 | Saturn Corporation | Open-loop clutch-to-clutch upshift control having clutch overlap regulation |
| US5580332A (en) | 1995-04-13 | 1996-12-03 | Caterpillar Inc. | Method for determining the fill time of a transmission clutch |
| US6088645A (en) | 1996-07-08 | 2000-07-11 | Komatsu Ltd. | Control device and control method for transmission with clutch |
| JP3524723B2 (en) | 1996-08-10 | 2004-05-10 | シーケーディ株式会社 | Electrically operated valve manifold |
| US6357229B1 (en) | 1997-01-22 | 2002-03-19 | Voith Turbo Gmbh & Co., Kg | Hydrodynamic clutch and method of operating a hydrodynamic clutch |
| US5941358A (en) | 1997-12-16 | 1999-08-24 | Caterpillar Inc. | End-of-fill detector arrangement for a fluid actuated clutch |
| US6115661A (en) | 1998-04-09 | 2000-09-05 | Caterpillar Inc. | End-of-fill detector for a fluid actuated clutch |
| US6205875B1 (en) | 1999-08-31 | 2001-03-27 | Case Corporation | Flow restrictor assembly in transmission clutch control system |
| US6292732B1 (en) | 2000-03-20 | 2001-09-18 | General Motors Corporation | Adaptive on-coming clutch fill control for an automatic transmission |
| DE10153722A1 (en) * | 2001-10-31 | 2003-05-22 | Volkswagen Ag | Method for shift control of a powershift transmission |
| US6640950B2 (en) | 2001-12-28 | 2003-11-04 | Caterpillar Inc. | Fluid clutch fill detection system and method |
| US6799108B2 (en) | 2002-04-08 | 2004-09-28 | General Motors Corporation | Control system and method for maintaining a constant engine idle speed of an automatic transmission-equipped vehicle |
| JP3784353B2 (en) | 2002-08-28 | 2006-06-07 | ジヤトコ株式会社 | Hydraulic control device for vehicle transmission |
| US7051856B2 (en) | 2003-11-04 | 2006-05-30 | General Motors Corporation | Method and apparatus for applying and releasing a clutch |
| US6915890B1 (en) | 2003-12-18 | 2005-07-12 | General Motors Corporation | Learning method for oncoming clutch fill level and volume |
| US20060089775A1 (en) | 2004-10-22 | 2006-04-27 | Whitton Matthew D | Method and apparatus for adaptive control of power-on downshifts in an automatic transmission |
| DE102006026600A1 (en) * | 2006-06-08 | 2007-03-29 | Zf Friedrichshafen Ag | Drive train operating method for motor vehicle, involves providing automatic transmission with five switching units, in which one of switching units is opened or closed during implementation of two stepping and/or shifting operations |
-
2007
- 2007-12-21 US US11/963,204 patent/US7909733B2/en not_active Expired - Fee Related
-
2008
- 2008-12-16 DE DE112008003449T patent/DE112008003449T5/en not_active Withdrawn
- 2008-12-16 CN CN2008801216947A patent/CN101903663A/en active Pending
- 2008-12-16 WO PCT/US2008/013758 patent/WO2009085151A1/en active Application Filing
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5722459A (en) * | 1995-05-31 | 1998-03-03 | Hyundai Motor Company | Pressure control valve of a hydraulic control system of an automatic transmission |
| US5913577A (en) * | 1996-12-09 | 1999-06-22 | Caterpillar Inc. | Pilot stage of an electrohydraulic control valve |
| EP1285806A2 (en) * | 2001-08-10 | 2003-02-26 | Caterpillar Inc. | Power take-off clutch control system |
| US6796329B1 (en) * | 2002-01-23 | 2004-09-28 | Trans-A-Matic | Compact fluid pressure control valve solenoid with pilot or gate valve |
| JP4806934B2 (en) * | 2005-01-31 | 2011-11-02 | アイシン精機株式会社 | Hydraulic control device for automatic transmission |
| CN1924387A (en) * | 2005-09-02 | 2007-03-07 | 通用汽车公司 | Clutch control regulator valve with end of fill detection |
Cited By (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103477127A (en) * | 2011-04-19 | 2013-12-25 | 马自达汽车株式会社 | Automatic transmission control method and control device, and automatic transmission system |
| US9062760B2 (en) | 2011-04-19 | 2015-06-23 | Mazda Motor Corporation | Automatic transmission control method and control apparatus, and automatic transmission system |
| CN103477127B (en) * | 2011-04-19 | 2015-09-02 | 马自达汽车株式会社 | The controlling method of automatic transmission and control gear and Transmission System |
| CN103122995A (en) * | 2011-11-18 | 2013-05-29 | 腓特烈斯港齿轮工厂股份公司 | Hydraulic valve system for actuating at least one shifting element of a transmission |
| CN103291906A (en) * | 2012-02-27 | 2013-09-11 | 腓特烈斯港齿轮工厂股份公司 | A method of determining an operating state of a form-locking shift element of a transmission apparatus |
| CN106471270A (en) * | 2014-06-17 | 2017-03-01 | 沃尔沃卡车集团 | Improved clutch control |
| CN106471270B (en) * | 2014-06-17 | 2019-05-10 | 沃尔沃卡车集团 | Improved clutch control |
| US10344809B2 (en) | 2014-06-17 | 2019-07-09 | Volvo Truck Corporation | Clutch control |
| CN105889357A (en) * | 2015-02-17 | 2016-08-24 | 通用汽车环球科技运作有限责任公司 | Compensation for drag force generated by rotating clutch piston seal |
| CN105889357B (en) * | 2015-02-17 | 2018-08-31 | 通用汽车环球科技运作有限责任公司 | Compensation to the drag caused by rotary clutch piston seal |
| CN107091322A (en) * | 2016-02-18 | 2017-08-25 | 通用汽车环球科技运作有限责任公司 | Pressure sensor for power output |
| CN107091322B (en) * | 2016-02-18 | 2019-04-12 | 通用汽车环球科技运作有限责任公司 | Pressure sensor for power output |
Also Published As
| Publication number | Publication date |
|---|---|
| WO2009085151A1 (en) | 2009-07-09 |
| US7909733B2 (en) | 2011-03-22 |
| DE112008003449T5 (en) | 2011-01-13 |
| US20090159389A1 (en) | 2009-06-25 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN101903663A (en) | Clutch end-of-fill detection strategy related solenoid valve | |
| KR100436278B1 (en) | The gear ratio selector mechanism | |
| US6705175B1 (en) | Gearshift control device for a transmission | |
| KR101302329B1 (en) | Clutch control device and clutch control method | |
| JP5874839B2 (en) | Brake device for transmission and control system therefor | |
| CN101713683B (en) | Apparatus and method for detecting end-of-fill at clutch in automatic transmission | |
| KR101283049B1 (en) | Auto Transmission Hydraulic Pressure Control Apparatus | |
| US6382248B1 (en) | Self-diagnosing pressure regulator apparatus | |
| JPH11508677A (en) | Hydraulic actuation system | |
| WO2015108637A2 (en) | Spool valve | |
| US9188219B2 (en) | Procedure for operating a transmission device, particularly a 9-speed-transmission | |
| US6115661A (en) | End-of-fill detector for a fluid actuated clutch | |
| US7275473B2 (en) | Hydraulic control apparatus for a shifting fork in a manual transmission | |
| KR20020013911A (en) | Method for operating an actuation device of an automated transmission | |
| US5941358A (en) | End-of-fill detector arrangement for a fluid actuated clutch | |
| EP2864675A1 (en) | Dual-wet-clutch transmission | |
| US6755766B2 (en) | Vehicle power transmission device | |
| WO2006107428A1 (en) | A system and method for controlling engagement of a clutch | |
| EP0947743B1 (en) | Gear ratio selecting apparatus for transmissions | |
| US20090249777A1 (en) | Transmission device with at least one form-fit shifting element being hydraulically actuated via a hydraulic system | |
| US20070028760A1 (en) | Pressure control system for a torque-transmitting mechanism | |
| JPH01224549A (en) | Hydraulic operating clutch controller | |
| US3550507A (en) | Hydraulic valve | |
| CN103270331A (en) | Method for controlling an actuator | |
| JP3432150B2 (en) | Control circuit for power shift transmission |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| C02 | Deemed withdrawal of patent application after publication (patent law 2001) | ||
| WD01 | Invention patent application deemed withdrawn after publication |
Application publication date: 20101201 |